US4526506A - Radial fan with backwardly curving blades - Google Patents

Radial fan with backwardly curving blades Download PDF

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Publication number
US4526506A
US4526506A US06/565,656 US56565683A US4526506A US 4526506 A US4526506 A US 4526506A US 56565683 A US56565683 A US 56565683A US 4526506 A US4526506 A US 4526506A
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Prior art keywords
blades
blade
radial
radial fan
cover plate
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Expired - Lifetime
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US06/565,656
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English (en)
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Friedrich Koger
Udo Haas
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Wilhelm Gebhardt GmbH
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Wilhelm Gebhardt GmbH
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Assigned to WILHELM GEBHARDT GMBH reassignment WILHELM GEBHARDT GMBH ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: HASS, UDO
Assigned to WILHELM GEBHARDT GMBH reassignment WILHELM GEBHARDT GMBH ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KOGER, FRIEDRICH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape

Definitions

  • the present invention is with respect to a radial fan made up of a spiral housing and a radial impeller therein, the impeller bearing blades running between a support plate and a cover plate having a rounded guide overlapping an inlet cowl of the fan.
  • the blades are designed in the form of airfoils (for example like the section of an airplane wing) having inner edges that are at a slope in relation to the axis of turning of the radial impeller.
  • the inner diameter of the blades becomes smaller from the cover plate to the support plate and the ratio of the mean inner diameter of the blades to the outer diameter thereof is about 0.7 to 1.
  • Such radial fans may be looked upon as the last stage in a process of development whose purpose was that of designing such fans to have the highest possible power density or power to size ratio while at the same time having a good efficiency and an overload-proof characteristic curve.
  • dimensionless numbers or coefficients have been widely used, that take into account the well-known relation between the volumetric flow V and the increase in pressure ⁇ p t and the diameter and the speed n of turning of the impeller and the density ⁇ of the medium to be impelled.
  • the volume number defined as ##EQU1## and the pressure number ##EQU2## put an end to these dependencies and made possible a direct comparison between radial fans with different size and performance data.
  • a radial fan may be described by a characteristic curve in the form of ⁇ t against ⁇ .
  • the optimum conditions of operation are produced at an optimum point characterized by the pair of values ⁇ topt , ⁇ opt , in which the efficiency ⁇ of the radial blower is at its maximum ⁇ max .
  • the power density at the optimum point that is to say the product of ⁇ topt and ⁇ opt may be used. Measured in terms of these magnitudes surprising results may be produced with the said form of fan in keeping with the prior art.
  • ⁇ max 0.85 ⁇ topt is 0.91 and ⁇ opt is equal to 0.2 so that the power density takes on a value of 0.182.
  • One purpose or object of the invention is to make a better design of a radial fan of the sort named while at the same time keeping the useful effects produced so far.
  • the power density at the optimum point is to be stepped up to a value greater than 0.2, while on the other hand the volume number or coefficient is not to go under 0.2 and the efficiency is to be 80% and over.
  • These requirements are in effect representative of an even more compact design of such a radial fan with the same or an even lower power requirement so that the fan is in keeping with the most exacting demands with respect to economy in the use of energy and profitability of plant.
  • any differences between the volume number ⁇ and ⁇ opt are to be possible with only the least possible change for the worse in the efficiency ⁇ .
  • a radial fan is so designed in the invention that the blade entry angle on the cover plate side is 4° to 7° smaller than the blade entry angle on the support plate side and the blade exit angle on the cover plate side is 3° to 6° smaller than the blade exit angle on the support plate side and the blade entry angle on the cover plate side is between 14° and 20° and the blade exit angle on the cover plate side is between 39° and 45°.
  • Twisted blades in the form of airfoils for use a blades in fans have been noted in the German Pat. No. 952,547, in which it was said that the entry edges of the blades might be skew and not parallel to the axis of the impeller.
  • the blade entry and exit angles were to be greater on the cover plate than on the support plate side; the purpose of the present invention would not be effected with such a design.
  • Curved or arched blades of like design are furthermore to be seen in the German Auslegeschrift specification No. 1,057,725, which furthermore is to the effect that such blades might be curved in the opposite direction and might be in the form of streamlined, airfoil-like structures.
  • there is nothing said in this earlier specification about keeping to the linear and angle ranges that are of key importance in the present invention.
  • FIG. 1 is a plan and partly broken away view of a radial fan in keeping with the present invention.
  • FIG. 2 is a section through the impeller of the radial fan taken on the line II--II of FIG. 1, in which, to make the figure more straightforward, only one pair of blades on each half of the impeller is to be seen without the shaft being figured.
  • FIG. 3 is a plan view of a twisted blade of the impeller as marked III in FIG. 1.
  • FIGS. 4 and 5 are views of further possible forms of blade as seen in a plan view like that of FIG. 3.
  • FIG. 6 is a view of a further possible form of the invention with an untwisted, sloping blade as seen in plan as in the view of FIG. 3.
  • FIG. 7 is a plot of the characteristic of a radial fan in keeping with the present invention to give the relation between ⁇ t and ⁇ on the one hand and ⁇ on the other.
  • FIG. 8 is a plot of the degree of reaction of the radial fan of the present invention at the optimum point in comparison with radial fans of the prior art.
  • a radial fan in keeping with the present invention has a spiral housing 1, in which a radial impeller 2 is fitted.
  • the said impeller 2 is supported on a shaft 3. It is turned by a drive (not figured) in the direction of the arrow 4.
  • a drive not figured
  • the fluid that is to be transported or moved by the fan is aspirated in the axial direction, that is to say in the axial direction of the shaft 3 so that such fluid is taken up into the spiral housing 1 and is then forced outwards therefrom in a radial direction.
  • the said fluid makes its way into the inside of the spiral housing 1 through an inlet nozzle or cowl 5.
  • the said cowl 5 is placed to the side on the spiral housing and it takes the form of a collar placed round the edge of an inlet opening and becoming narrower in an inward direction like a funnel.
  • the inner edge 7 of the inlet cowl 6 in this respect takes the form of a generally cylindrical sleeve, the same forming a part of the inlet cowl 5 overlapping a cover plate 8 forming a casing round the radial impeller 2.
  • the inlet cowl 5 will be seen to be placed radially within the cover plate 8. Between the inlet cowl 5 and the part 9 overlapping same of the cover plate 8 there is a gap 10.
  • the cover plate 8 will be seen to be running outwards in the form of a curved contour or guide 11 in a radially outward direction.
  • the guide 11 comes to an end at the top side 12 of a number of blades 13, which for their part have their lower side 14 fixed on a support plate 15 of the radial impeller 2.
  • the blades are backwardly curved and in the form of airfoils, of which more details will be given hereinafter.
  • the fluid aspirated into the radial impeller 2 by way of the inlet cowl 5 is forced by the blades 13 in a radial direction and guided in the spiral housing 1 out towards an outlet area with a more specially rectangular cross section, the fluid then moving out of the radial fan through said area.
  • FIG. 2 the reader will see a form of the fan of the present invention designed for aspiration of the fluid on both sides, such fan being more specially used for fitting in air conditioning units and plant.
  • the radial fan is symmetrical about a middle plane, in which the support plate 15 of the radial impeller 2 is placed.
  • the support plate 15 is fitted on both sides with blades 13, which on their top sides 12 are in each case covered over by a cover plate 8.
  • Each of the inlet cowls 5 has a round guide 11 overlapping with the inlet cowl next thereto, there then being a space therebetween in the form of a gap 10.
  • Each of the sides of the radial impeller 2 on the support plate 15 does for this reason have an aspirating effect in the axial direction, such aspiration causing flows of fluid, heading towards each other, to be moved through the side walls 17 and 18 into the radial fan.
  • the flows of fluid are forced outwards in a radial direction into the common spiral housing 1. They come out of it by way of an outlet area 16.
  • the sides of the radial impeller 2 are in this design made completely symmetrical; dimensions marked in FIG. 2 on the one half only are for this reason used in the other half or sides of the radial fan as well.
  • the outline of the blades 13 is the same on the two halves of the radial impeller 2.
  • the inner edges 19 of the blades are on a surface of rotation centered on the axis of turning of the radial impeller 2, said surface becoming narrower like a funnel from the cover plate 8 towards the support plate 15.
  • the surface of rotation thought of as having the outer edges 20 of the blades on it is on the other hand cylindrical.
  • the outline or outer contour of the blades 13 may for this reason be described over its full height between the cover plate 8 and the support plate 15 in terms of a generally constant blade outer diameter d 2 .
  • the blades 13 are as such twisted so that the inner edges 19 and the outer edges 20 of the blades are skewed on the surfaces of rotation enveloping them, or in other words they are not parallel to the axis of turning of the radial impeller 2.
  • FIG. 1 in FIG. 3 as well the blade 13 is being viewed looking down onto the support plate 15.
  • the cover plate 8 otherwise fixed on the top ends 12 of the blades 13 has been taken off.
  • the lower ends 14 (that will be seen to be partly covered over) of the blade 13 is fixed to the support plate 15. Because of the twisted form of each blade 13 there is a change of the blade entry angle ⁇ 1 and of the blade exit angle ⁇ 2 with the height of the radial impeller.
  • the blade entry angle ⁇ 1 is defined in planes that are parallel to the support plate 15. The angle is in each case formed between an airfoil middle or center line 21 of the blade 13 on the one hand and a tangent 23 to the surface of rotation formed by the blade inner edges 19 on the other hand. In the same planes parallel to the support plate 15 the blade exit angle ⁇ 2 is defined as well. It is formed in each case between one airfoil middle line 24 of the blade 13 on the one hand and a tangent 26 to the surface of rotation described by the outer edges 20 of the blades on the other hand.
  • the blade entry angle ⁇ 1 D on the cover plate side and the blade exit angle ⁇ 2 D on the cover plate side have been marked at the level of the cover plate 8.
  • the blade entry angle ⁇ 1 on the support plate side and the blade exit angle ⁇ 2 T on the same side, on the other hand are marked at the level of the support plate 15.
  • ⁇ 1 D is smaller than ⁇ 1 T and furthermore ⁇ 2 D is smaller than ⁇ 2 T .
  • the blade 13 has an airfoil form that is of special value in connection with the desired flow or aerodynamic properties.
  • the airfoil form may be seen specially clearly at the top cover plate side 12 and the support plate lower side 14 of the said blade.
  • the airfoil form is like that of the wing of an airplane designed for low speeds, that is to say speeds up to about 250 km/h.
  • the blade 13 has such an airfoil form over its full height, that is to say between the cover plate 8 and the support plate 15. Every section taken through a blade 13 in a plane parallel to the support plate 15 will for this reason have the same section as that of an airfoil of the sort noted.
  • the desired high power concentration of the radial fan is made possible inasfar as with a ratio of the mean inner blade diameter d 1 to the outer diameter of the blade d 2 of about 0.7 to 1 the blades 13, made with the form of a airplane wing profile, are so designed that the cover plate side blade entry angle ⁇ 1 D is 4° to 7° smaller than the support plate side blade entry angle ⁇ 1 T . And furthermore the cover plate side blade exit angle ⁇ 2 D is 3° to 6° smaller than the support plate side exit angle ⁇ 2 T , while the cover plate side blade entry angle ⁇ 1 D is between 14° and 20° and the cover plate side blade exit angle ⁇ 2 D is between 39° and 45°.
  • Wide ranging tests have now made it clear that with sizes in the given range the best performance data for a radial fan may be produced.
  • the given angle ratios may be produced by twisting the blades 13 or in other ways.
  • cover plate side blade entry angle ⁇ 1 D is equal to 14.5° to 17.5° and the support plate side blade entry angle ⁇ 1 T is 21.5°, whereas the cover plate side blade exit angle ⁇ 2 D is equal to between 40° and 43°.
  • the cover plate side blade exit angle ⁇ 2 T is equal to 46°.
  • the blade form to be seen in FIG. 3 is produced by twisting about a twist axis 22 running normally to the plane of the figure.
  • the twist axis 22 is for this reason parallel to the axis of turning of the radial impeller 2. It is placed in a middle part of the blade 13.
  • the angle ratios noted herein may furthermore be produced if the twist axis 22 of the blade 13 is at the outer edges 20 of the blades.
  • FIG. 4 is viewed in FIG. 4, in which again the structure is to be seen looking in the same direction as in FIG. 3. Parts with the same function as in FIG. 3 are given the same part numbers.
  • the blade 13 to be seen here has an airfoil like section and is curved backwards. It outer edge 20 is parallel to the axis of turning of the radial impeller 2 so that it may be thought of stretching upwards from the plane of the paper.
  • the axis 22 of twist is at the outer edge of the blade 13. Because of the twisted form of the blade the entry edge 19 is at a slope in relation to the axis of turning of the radial impeller 2 and the inner diameter of the blade may be seen to be different at different levels of the blade as was the case in FIG. 3. It will be seen in the system of FIG.
  • the given angle ratios may as well be produced by twisting about a twist axis 22, that is near or at the outer edges 20.
  • FIG. 5 the reader will see a further possible working example of a twisted blade 13.
  • the twist axis 22 running parallel to the twist axis of the radial impeller 2 is placed in the middle part of the blades 13.
  • the blade inner edge 19 is at such a slope that the surface thought of as enveloping all the blade inner edges 19 takes the form of a cone becoming narrower from the cover plate 8 to the support plate 15. That is to say, the inner diameter of the blades as measured at the level of the cover plate 8 is greater than at the level of the support plate 15.
  • the outer edge 20 of the blades 13 is placed at a slope or angle in the same sort of way because of the twist about the twist axis 22.
  • the surface of rotation eveloping all the blade outer edges 20 has the form of a conical face becoming wider from the cover plate 8 to the support plate 15.
  • the blade's outer edge is not formed by a single blade outer diameter d 2 that is more or less unchanging right over the full height of the blade 13.
  • FIG. 6 is a view of a still further possible form of blade, which is not based on a twisted from of the blades airfoil but on a deformation by shearing normal to the length direction of the blade 13. Because of this shearing effect the blade 13 is at a slope, when looked at from the cover plate 8 towards the support plate 15, in a direction opposite to the direction of turning of the radial impeller 2.
  • the outer edges 20 of the blades in this case have a generally constant diameter d 2 over the height of the blades 13.
  • the inner edges 19 of the blades are put at such a slope, because of the deforming or shearing effect, that the surface enveloping them or their envelope curve takes the form of a funnel-like surface of rotation becoming narrower from the cover plate 8 to the support plate 15.
  • the blade 13 does for this reason have a large diameter to its inner edge 19 at the level of the cover plate 8 than at the support plate 15.
  • a line normal to the support plate 15 running to the blade's inner edge 19 will be at an acute angle to the inner blade edge 19 not only in a tangential but furthermore in a radial projection with respect to the axis of rotation of said fan.
  • the angle ratios in keeping with the present invention may furthermore be produced by a shearing or deforming effect on an airfoil-like backwardly curved blade 13 and not only by twisting.
  • geometrical operations may be used for this purpose in which the blade inner edges 19, that in the first place were lined up parallel to the axis of turning of the radial impeller 2, and the blade outer edges 20 are changed so as to be on the skew in relation to the axis of turning.
  • the system of the invention may be so structured that the chords of the airfoils at sections through the blades along the blade width are in different planes perpendicular to the support plate 15 relative to the main radial direction of flow at the chord.
  • the present invention makes possible a radial fan whose power density, that is to say the product of ⁇ opt and ⁇ topt is greater than 0.2 at a volume number ⁇ opt of approximately 0.2 and more and for this reason is greater than the density in all prior art radial fans.
  • the volume number range ⁇ 0 .8 within which the radial fan may be run with an efficiency of more than 80%, has been increased so that it is better than the prior art at both sides or edges of the range by at least 20%.
  • the efficiency ⁇ has been plotted against ⁇ using a separate scale.
  • the efficiency ⁇ gets to its higher value ⁇ max at a volume number of coefficient ⁇ opt of 0.215.
  • the parallel value ⁇ topt is over 0.94 so that the power density as the product of ⁇ opt and ⁇ opt is over 0.2.
  • ⁇ max of efficiency the same only goes down a very small amount in relation to the increasing and decreasing volume number ⁇ .
  • the invention does in fact make possible a radial fan that is much more compact that has so far been possible in the prior art, the fan furthermore running with a high efficiency even clear of the optimum point or position.
  • the fan has the best or optimum performance data.
  • one size or dimension important for the invention is the entry diameter d 0 of the cover plate 8, that is to say the smallest diameter of its inlet part.
  • the entry diameter d 0 is marked in FIG. 2.
  • the ratio between it and the outer diameter d 2 of the blades is to be about 0.75 to 1.
  • a further item of design that is important for the radial fan of the invention is furthermore the form of the guiding contour 11 of the cover plate 8.
  • This plate is in the form of a conic section, that is to say circular, parabolic or hyperbolic and is for this reason described by one or more radiuses of curvature r (FIG. 2).
  • FIG. 2 a circular curvature of the guide contour 11 will be seen with one single radius r of curvature.
  • the radius or radiuses of curvature r have to have of ratio to the entry diameter d 0 within a range of 0.2:1 to 0.3:1.
  • the exit width b 2 of the radial fan that is to say the distance between the support plate 15 and the cover plate 8 at the blade exit edge 20.
  • the exit width b 2 in the case of the radial fan with aspiration on the two sides thereof as in FIG. 2 is in each case related to one half side of the radial impeller 2.
  • the ratio of the exit width b 2 to the outer diameter of the blades d 2 is to be in a range of 0.225:1 to 0.275:1 and more specially it is to be 0.25:1.
  • the exit area F 2 of the radial fan may be used, that is to say the size of the area of the cylindrical envelope curve of the blade outer edges 20.
  • the outlet or exit area F 2 is defined by the exit width b 2 and the outer blade diameter d 2 . It is best related to the entry area F 0 of the radial impeller 2, that is to say the clearance width of the inlet part of the cover plate 8 with the entry diameter d 0 .
  • the ratio of the entry area F 0 of the radial impeller 2 to its exit area F 2 is to be in a range of 0.51:1 to 0.62:1 and more specially is to have a value of 0.56:1.
  • the optimum dimensions or proportions of the radial fan in keeping with the invention lastly have to take into account the ratios between the different dimensions of the spiral housing 1, in which respect the entry area F E of the inlet cowl 5 and the cross section F A of the exit area 16 of the spiral housing are of interest.
  • the size of the exit area F A is marked in FIG. 1 and the clearance width F E of the inlet cowl 5 is marked in FIG. 2.
  • the ratio of F E to F A is to be in a range of 0.67:1 to 0.71:1, the preferred value being 0.69:1
  • the number of the blades 13 spaced out round and on the radial impeller is to be between 10 and 16. In a preferred form of the invention there are 12 blades 13.
  • the radial fan in keeping with the invention makes possible a very high degree of reaction, that is to say the quotient of static pressure/overall pressure. Because this is so the proportion of the kinetic energy that at first may not be used is very small.
  • FIG. 8 makes possible a comparison between the radial fan in keeping with the invention and such fans of the prior art. In this respect the degree of reaction is plotted against the volume numbrer ⁇ at the highest efficiency ⁇ max , that is to say at the optimum point ⁇ opt . It will be seen that prior art fans have values of 1 to 13 and a fan of the invention has a value of 14 and that the value of 14 in keeping with the invention is the best possible compromise between the need for the highest possible volume number and a high degree of reaction.
  • the invention makes possible an apparatus in which the shaft horsepower takes on a maximum value within the given volume number range covered, that is to say it becomes possible for the driving motor of the radial fan to be designed to be in harmony with the maximum of the shaft power so that on running the fan under conditions that are different to the operating point for which it was designed overloading is not to be feared.
  • the radial fan or blower in keeping with the invention may be said to have the edge over a drum impeller fan with forwardly curving blades, in the case of which the shaft power goes up with an increase in the volume flow, that is to say with an increase in the volume number ⁇ , progressively, and there is no maximum at all. Because of this there will always be a danger of overloading the motor driving such a fan.
  • the characteristic curve of a fan in keeping with the invention is highly dependent on the blade angles and the twist of the blades.
  • ⁇ max was 0.79, it falling short of 0.8.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Jet Pumps And Other Pumps (AREA)
US06/565,656 1982-12-29 1983-12-27 Radial fan with backwardly curving blades Expired - Lifetime US4526506A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP82112081A EP0112932B1 (de) 1982-12-29 1982-12-29 Radialventilator mit rückwärts gekrümmten, profilierten Schaufeln
EP82112081.3 1982-12-29

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EP (1) EP0112932B1 (de)
AT (1) ATE13711T1 (de)
DE (1) DE3264089D1 (de)

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US4900228A (en) * 1989-02-14 1990-02-13 Airflow Research And Manufacturing Corporation Centrifugal fan with variably cambered blades
US4917572A (en) * 1988-05-23 1990-04-17 Airflow Research And Manufacturing Corporation Centrifugal blower with axial clearance
DE9303711U1 (de) * 1993-03-13 1993-05-13 Babcock-BSH AG vormals Büttner-Schilde-Haas AG, 4150 Krefeld Radiallaufrad
GB2289090A (en) * 1994-05-06 1995-11-08 Philips Electronics Uk Ltd Centrifugal fan
GB2337795A (en) * 1998-05-27 1999-12-01 Ebara Corp An impeller with splitter blades
US6217285B1 (en) * 1996-08-08 2001-04-17 Sanyo Electric Co., Ltd. Impeller for a centrifugal blower
CN1078317C (zh) * 1994-04-28 2002-01-23 东陶机器株式会社 多叶片径流式通风机的设计方法与多叶片径流式通风机
US20030182954A1 (en) * 2002-03-30 2003-10-02 Parker Danny S. High efficiency air conditioner condenser fan
WO2004015275A1 (en) * 2002-08-02 2004-02-19 Spal S.R.L. A centrifugal fan impeller with blades inclined relative to the axis of rotation
US6739835B2 (en) * 2001-08-24 2004-05-25 Lg Electronics Inc. Blade part in turbofan
US20040165986A1 (en) * 2002-03-30 2004-08-26 Parker Danny S. High efficiency air conditioner condenser fan with performance enhancements
US20050074326A1 (en) * 2003-10-02 2005-04-07 Torrington Research Company Muffler for impeller with rearwardly curved blades
US20050191174A1 (en) * 2004-02-27 2005-09-01 Ling-Zhong Zeng Centrifugal fan
US7044720B1 (en) * 2004-12-10 2006-05-16 Toshiba Home Technology Corporation Fan motor
US20070050898A1 (en) * 2005-08-09 2007-03-08 Larson Keith A Surgical protective system and assembly having a head gear assembly supporting a surgical garment and air delivery system
CN100376804C (zh) * 2002-08-23 2008-03-26 罗伯特-博希股份公司 用于为电机输送冷空气的径向风机叶轮
WO2008047962A1 (en) 2006-10-19 2008-04-24 Lg Electronics Inc. Turbo fan for blowing and refrigerator having the same
US20100329871A1 (en) * 2008-02-22 2010-12-30 Horton, Inc. Hybrid flow fan apparatus
US7937775B2 (en) 2005-08-09 2011-05-10 Microtek Medical, Inc. Surgical protective head gear assembly including high volume air delivery system
US20110284190A1 (en) * 2009-01-30 2011-11-24 Sanyo Electric Co., Ltd. Centrifugal air blower and air conditioner
CN102536896A (zh) * 2012-03-22 2012-07-04 安徽安风风机有限公司 一种离心风机的叶片
US20130170945A1 (en) * 2011-12-29 2013-07-04 Rbc Horizon, Inc. Furnace air handler blower with enlarged backward curved impeller and associated method of use
CN104093988A (zh) * 2011-11-17 2014-10-08 株式会社日立制作所 离心式流体机械
US9022731B2 (en) 2009-11-03 2015-05-05 Alessandro Seccareccia Centrifugal ceiling fan
JP2016061241A (ja) * 2014-09-18 2016-04-25 三菱重工業株式会社 遠心羽根車及び遠心圧縮機
EP2698542A3 (de) * 2012-08-14 2017-07-12 Ebm-Papst St. Georgen Gmbh & Co. Kg Radiallüfter mit Spiralgehäuse
US20170321930A1 (en) * 2016-05-09 2017-11-09 Stiebel Eltron Gmbh & Co. Kg Electric heating fan
EP3772592A1 (de) * 2019-08-08 2021-02-10 ebm-papst Mulfingen GmbH & Co. KG Radialgebläse für einen dunstabzug

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DE3264089D1 (en) 1985-07-11
EP0112932A1 (de) 1984-07-11
ATE13711T1 (de) 1985-06-15
EP0112932B1 (de) 1985-06-05

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